US4228662A - Cryogenic apparatus - Google Patents

Cryogenic apparatus Download PDF

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Publication number
US4228662A
US4228662A US06/010,677 US1067779A US4228662A US 4228662 A US4228662 A US 4228662A US 1067779 A US1067779 A US 1067779A US 4228662 A US4228662 A US 4228662A
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US
United States
Prior art keywords
valve
sleeve
exhaust system
plunger
cryogenic apparatus
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US06/010,677
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English (en)
Inventor
Gustav Klipping
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Deutsches Zentrum fuer Luft und Raumfahrt eV
Original Assignee
Deutsche Forschungs und Versuchsanstalt fuer Luft und Raumfahrt eV DFVLR
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Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D3/00—Devices using other cold materials; Devices using cold-storage bodies
    • F25D3/10—Devices using other cold materials; Devices using cold-storage bodies using liquefied gases, e.g. liquid air

Definitions

  • This invention relates to cryogenic apparatus for cooling objects to and maintaining them at a very low temperature in which by the use of the confinement produced by the thermomechanical effect superfluid helium II is evaporated from a supply container through a throttle element having a narrow passage into an evacuable system.
  • This plug enclosed in a holder having good thermal conductivity, is positioned at the point of connection of an exhaust system with the supply container and forms a throttle element which, although continuously permitting evaporation of a certain proportion of the liquid, determined by the total cross-section of the pores, and thus enabling a correspondingly limited refrigerating capacity to be achieved, nevertheless affords passage to the helium II liquid only when the inlet temperature at the plug is lower than the outlet temperature and when the pressure on the inlet side is lower than the pressure at the outlet side. With these conditions reversed, the passage of helium II liquid through the plug is completely blocked (thermomechanical effect).
  • a porous plug of this kind thus possesses valve properties that are dependent upon temperature and pressure.
  • the valve may have an additional control range in which the gap width is greater than 10 ⁇ m and may extend to a fully open position. Since, in contrast with porous plugs, the valve can permit unimpeded passage of helium I and gaseous helium, and since the throughput quantities of both media can be regulated virtually as required, dangers due to sudden excess pressure are eliminated, and the supply of refrigerating medium can be fully utilized, this being accompanied by an almost unlimited refrigerating capacity. The use of this valve also offers advantages when it is not, or is only intermittently, in contact with the liquid as is the case when the content in the supply container diminishes.
  • the valve element can be constituted by a cylindrical valve plunger which, with the valve sleeve, forms an annular gap having a width of less than 10 ⁇ m and which is mounted to be axially displaceable in the valve sleeve.
  • the valve plunger may be so shaped that, in conjunction with the valve sleeve, it defines a width of gap greater than 10 ⁇ m in an end portion of its path of travel.
  • the end of the valve plunger is advantageously tapered, or one or more tapered recesses, which may be arranged symmetrically, are formed in the end of the valve plunger.
  • the valve sleeve has, at at least one end, at least one recess which is parallel with its axis and extends into an annular channel formed between its ends.
  • the valve can be used both with an annular gap of below 10 ⁇ m, and with the extended passage cross-section for admitting liquid.
  • the exhaust system may be provided with at least one heat-exchanger which is arranged in the supply container in such a way that it is in heat-exchange relationship with the refrigerating medium.
  • the liquid helium II exhibits, at low temperatures, a specific heat which is greater than that of all solid materials to the extent of several orders of magnitude.
  • the refrigeration capacity occurring at the outlet side of the valve and produced as a result of complete evaporation of a double-phase mixture (helium II--droplets in helium gas), can be carried back to the refrigerating medium.
  • a particularly great constancy in temperature is achieved in the object to be cooled, which may be connected to the cooling medium through heat-conducting holders, supply lines, bridges or the like.
  • the exhaust system When a heat-exchanger is arranged in contact with the object to be cooled and is located in the object chamber, it may be expedient for the exhaust system to be split into two lines, one line including at least one heat-exchanger in the supply container for the refrigerating medium, the other line including a heat-exchanger connected to the object to be cooled. In such case means may be provided for evacuating the two lines differentially.
  • FIG. 2 illustrates an alternative form of valve comprising a valve plunger having a tapered portion
  • FIGS. 3 and 4 illustrate another form of valve having a plunger with symmetrically disposed tapered recesses
  • FIGS. 5 and 6 illustrate a further form of valve which has recesses and annular channels in its sleeve
  • FIG. 8 shows a cryogenic apparatus according to this invention which incorporates a heat-exchanger on the object to be cooled.
  • the cryogenic apparatus shown in FIG. 1 which is for cooling an object in the temperature range below 2° K., comprises a supply container 1 for accommodating a refrigerating medium 2 which contains superfluid helium II.
  • the supply container 1 is surrounded by radiation shields 3 and, together with these, is placed in a vacuum jacket container 4.
  • the necessary connections for evacuation and for introducing the supply of refrigerating medium are of the usual design and are therefore not shown in detail in the drawings.
  • An object 5 to be cooled is arranged within a cooled chamber 6, in contact with one of the cold walls thereof, and this chamber can likewise be evacuated.
  • the valve forming the throttle element consists of a sleeve 7, in which a cylindrical valve plunger 8 is axially displaceable.
  • the width of the annular gap between the valve plunger 8 and the interior wall of the sleeve 7 is less than 10 ⁇ m.
  • the valve sleeve is open to the refrigerating medium 2 in container 1 and its other end is connected to an exhaust system through a pipe 9 into which is connected a heat-exchanger 10 which is located in the refrigerating medium 2 in the container 1.
  • an inner bellows element 12 is provided, through the end plates 13 of which extends a vacuum-sealed valve stem 14.
  • the valve stem 14 which, in the known manner, can be provided with displaceable intermediate portions which facilitate movement of the valve plunger and/or reduce the passage of heat by conduction, extends outwardly through openings in the radiation shields 3 and into the vacuum jacket container 4 by way of an outer bellows element 15 so that a gland-less seal is achieved.
  • the movement of the valve stem 14 and therefore the control movement of the valve plunger 8 is effected by an electrodynamic or electromagnetic drive unit 16 which may be designed, for example, to operate in the manner of the moving coil of a loudspeaker or the plunger of a solenoid.
  • the drive unit 16 is so controlled by way of regulating means 17 in dependence upon the temperature of the refrigerating medium 2 as determined by a sensor 18, that the regulating system ensures a constant temperature in the refrigerating medium 2.
  • FIGS. 2, 3 and 4, and 5 and 6 illustrate alternative forms of the valve of FIG. 1.
  • a tapered portion 19 is provided at the free end of the plunger 8.
  • FIGS. 3 and 4 show a cylindrical valve plunger 8 which has tapered recesses 20 evenly distributed around its periphery at its free end.
  • a more efficient guiding of the valve plunger 8 in the sleeve 7 is achieved as compared with the FIG. 2 arrangement.
  • FIGS. 1 In the arrangement illustrated in FIGS.
  • valve plunger 8 is cylindrical, and in the valve sleeve 7 are formed recesses 21 and 22, which, at both ends of the sleeve extend axially over part of its length, and which communicate with annular grooves 23 and 24 respectively.
  • the valve can operate over an additional control range in which the effective width of the annular gap is above 10 ⁇ m.
  • FIG. 7 shows a modification of the apparatus of FIG. 1, which in addition to the heat-exchanger 10, disposed in the refrigerating medium 2, incorporates an additional heat-exchanger 25 which is in direct contact with an object 26 to be cooled.
  • the exhaust pipe 9 is divided into two parallel lines 27 and 28 which can be evacuated separately. This provides the possibility of effecting regulation in two regulating systems, the first of these systems being controlled by the sensor 18 of the FIG. 1 arrangement, whereas the second system comprises a further temperature sensor 29 on the object 26 to be cooled, in conjunction with a regulating device 30 which controls a vacuum valve 31 in the exhaust line 28 in such a way that the temperature of the object 26 to be cooled can also be kept constant.
  • valve 7, 8 is controlled in dependence upon the temperature of the object as determined by the temperature sensor 29.
  • the sensor 18 in the refrigerating medium 2 is here used only to control the valve 7, 8, during the cooling and filling of the entire system.
  • the refrigerating capacity available in the system and corresponding to the heat of evaporation of the evaporating helium II can be regulated in a very sensitive manner in this phase of the operation by varying the length of the annular gap. i.e. by displacing the valve plunger 8 in the sleeve 7, the annular gap remaining constant. Because of the very great thermal conductivity of helium II, a quantity of heat passing from the exterior or from the object to be cooled is immediately evenly distributed in the refrigerating medium, so that, by way of the sensor 18, the temperature of this medium can be used for controlling the valve.
  • a further operating phase occurs when, with helium II superposed on the valve, it is necessary to create a greater refrigerating capacity than the maximum that is possible when using a constant annular gap with the flow of liquid cut off.
  • the valve in the forms illustrated in FIGS. 2 to 6 can be operated in an additional control range wherein the width of gap is more than 10 ⁇ m, and liquid in quantities corresponding to the required refrigerating capacity can be released in controlled amounts into the exhaust-system.
  • This liquid vaporises completely in the heat-exchanger 10, which is positioned in the refrigerating medium 2. In this way, fluctuating as well as large changes in thermal load can be evened out with little inertia.
  • FIGS. 7 and 8 operates in accordance with the same basic principles. The only differences to be observed here relate to the discharging of the exhaust gas and the arrangement of the heat exchanger in relation to the object to be cooled.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Containers, Films, And Cooling For Superconductive Devices (AREA)
US06/010,677 1978-02-17 1979-02-06 Cryogenic apparatus Expired - Lifetime US4228662A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2806829 1978-02-17
DE2806829A DE2806829C3 (de) 1978-02-17 1978-02-17 Vorrichtung zur Tiefstkühlung von Objekten

Publications (1)

Publication Number Publication Date
US4228662A true US4228662A (en) 1980-10-21

Family

ID=6032278

Family Applications (1)

Application Number Title Priority Date Filing Date
US06/010,677 Expired - Lifetime US4228662A (en) 1978-02-17 1979-02-06 Cryogenic apparatus

Country Status (11)

Country Link
US (1) US4228662A (fr)
JP (1) JPS6051624B2 (fr)
BE (1) BE874233A (fr)
CA (1) CA1082473A (fr)
CH (1) CH624476A5 (fr)
DE (1) DE2806829C3 (fr)
FR (1) FR2417733A1 (fr)
GB (1) GB2015140B (fr)
IT (1) IT1114963B (fr)
LU (1) LU80932A1 (fr)
NL (1) NL177043C (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4510758A (en) * 1983-06-20 1985-04-16 Canberra Industries, Inc. Convertible cryostat
US4526015A (en) * 1984-10-15 1985-07-02 General Electric Company Support for cryostat penetration tube
US4546609A (en) * 1983-05-30 1985-10-15 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Apparatus for providing a continuous stream of a cryogenic liquid and in particular liquid nitrogen
US4635451A (en) * 1986-02-04 1987-01-13 General Electric Company Spring loaded valve for adding cryogenic liquid to a cryostat
US4635450A (en) * 1986-02-04 1987-01-13 General Electric Company Compact retractable cryogenic leads
DE3619580A1 (de) * 1986-06-11 1987-12-17 Licentia Gmbh Kryogene kuehlvorrichtung
US4779017A (en) * 1987-10-13 1988-10-18 The United States Of America As Represented By The Secretary Of The Air Force Superconducting rotor cooling system
US4869077A (en) * 1987-08-21 1989-09-26 Hypres, Inc. Open-cycle cooling apparatus
US5385027A (en) * 1993-08-19 1995-01-31 Apd Cryogenics, Inc. Continuous flow cryogen sublimation cooler
US5564067A (en) * 1989-07-05 1996-10-08 Alabama Cryogenic Engineering, Inc. Controlled-porosity trapping plugs for space cryogen system phase separators
US5779089A (en) * 1996-07-26 1998-07-14 Forma Scientific, Inc. Cryogenic storage apparatus with lid vent
WO2008064140A2 (fr) * 2006-11-17 2008-05-29 Thomas Michael R Système de refroidissement cryogénique
US20130283823A1 (en) * 2009-11-03 2013-10-31 The Aerospace Corporation Multistage pulse tube coolers

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3406859C1 (de) * 1984-02-25 1985-04-04 Messerschmitt-Bölkow-Blohm GmbH, 8012 Ottobrunn Vorrichtung zur Tiefstkühlung von Objekten
DE3529391A1 (de) * 1985-08-16 1987-03-05 Kernforschungsz Karlsruhe Verfahren zum kuehlen eines objektes mit hilfe von suprafluidem helium (he ii) und einrichtung zur durchfuehrung des verfahrens
DE3530168C1 (de) * 1985-08-23 1986-12-18 Messerschmitt-Bölkow-Blohm GmbH, 8012 Ottobrunn Regelbarer Helium-II-Phasentrenner
FR2598206B1 (fr) * 1986-05-05 1988-07-08 Air Liquide Refroidisseur joule-thomson.
FR2599128A1 (fr) * 1986-05-26 1987-11-27 Air Liquide Procede d'alimentation d'un refroidisseur joule-thomson et appareil de refroidissement pour sa mise en oeuvre
DE19625748C2 (de) * 1996-06-27 1999-09-02 Inst Luft Kaeltetech Gem Gmbh Vorrichtung zur Kühlung elektronischer Bauteile, vorzugsweise Sensoren
KR100394962B1 (ko) * 2001-04-11 2003-08-19 한국표준과학연구원 헬륨가스냉동기 및 연속냉각냉동기가 결합된 저온항온조
DE102004037837B3 (de) * 2004-08-04 2006-05-11 Universität Augsburg Vorrichtung zur Schaffung einer evakuierten Tieftemperaturumgebung für eine Probe und Verwendung der Vorrichtung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3472038A (en) * 1967-04-22 1969-10-14 Philips Corp Apparatus and method for transferring heat from a lower temperature level to a higher temperature level
US3667246A (en) * 1970-12-04 1972-06-06 Atomic Energy Commission Method and apparatus for precise temperature control
US3722581A (en) * 1970-10-23 1973-03-27 Bell Telephone Labor Inc Heat exchanger with adjustable conduit transit size for carrier
US3845636A (en) * 1970-06-26 1974-11-05 Philips Corp Control device for maintaining the level of a liquified gas in a container between two different limits

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1047424A (fr) * 1962-06-08
DE1501291A1 (de) * 1966-12-24 1969-12-04 Max Planck Gesellschaft Vorrichtung zur Nachfuellung eines Heliumbades bei Temperaturen bis unterhalb des ?-Punktes und Betriebsverfahren hierzu
NL6708719A (fr) * 1967-06-22 1968-12-23
GB1472333A (en) * 1973-10-18 1977-05-04 Max Planck Gesellschaft Method and apparatus for producing predetermined temperatures with the aid of a cryoliquid
GB1482601A (en) * 1974-09-11 1977-08-10 Knights P Internal combustion engines

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3472038A (en) * 1967-04-22 1969-10-14 Philips Corp Apparatus and method for transferring heat from a lower temperature level to a higher temperature level
US3845636A (en) * 1970-06-26 1974-11-05 Philips Corp Control device for maintaining the level of a liquified gas in a container between two different limits
US3722581A (en) * 1970-10-23 1973-03-27 Bell Telephone Labor Inc Heat exchanger with adjustable conduit transit size for carrier
US3667246A (en) * 1970-12-04 1972-06-06 Atomic Energy Commission Method and apparatus for precise temperature control

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4546609A (en) * 1983-05-30 1985-10-15 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Apparatus for providing a continuous stream of a cryogenic liquid and in particular liquid nitrogen
US4510758A (en) * 1983-06-20 1985-04-16 Canberra Industries, Inc. Convertible cryostat
US4526015A (en) * 1984-10-15 1985-07-02 General Electric Company Support for cryostat penetration tube
US4635451A (en) * 1986-02-04 1987-01-13 General Electric Company Spring loaded valve for adding cryogenic liquid to a cryostat
US4635450A (en) * 1986-02-04 1987-01-13 General Electric Company Compact retractable cryogenic leads
DE3619580A1 (de) * 1986-06-11 1987-12-17 Licentia Gmbh Kryogene kuehlvorrichtung
US4869077A (en) * 1987-08-21 1989-09-26 Hypres, Inc. Open-cycle cooling apparatus
US4779017A (en) * 1987-10-13 1988-10-18 The United States Of America As Represented By The Secretary Of The Air Force Superconducting rotor cooling system
US5564067A (en) * 1989-07-05 1996-10-08 Alabama Cryogenic Engineering, Inc. Controlled-porosity trapping plugs for space cryogen system phase separators
US5385027A (en) * 1993-08-19 1995-01-31 Apd Cryogenics, Inc. Continuous flow cryogen sublimation cooler
WO1995005567A1 (fr) * 1993-08-19 1995-02-23 Apd Cryogenics Inc. Dispositif de refroidissement par sublimation d'un cryogene a ecoulement continu
US5779089A (en) * 1996-07-26 1998-07-14 Forma Scientific, Inc. Cryogenic storage apparatus with lid vent
US6036045A (en) * 1996-07-26 2000-03-14 Forma Scientific, Inc. Cryogenic storage apparatus with lid vent
WO2008064140A2 (fr) * 2006-11-17 2008-05-29 Thomas Michael R Système de refroidissement cryogénique
WO2008064140A3 (fr) * 2006-11-17 2008-07-24 Michael R Thomas Système de refroidissement cryogénique
US20130283823A1 (en) * 2009-11-03 2013-10-31 The Aerospace Corporation Multistage pulse tube coolers
US9714776B2 (en) * 2009-11-03 2017-07-25 The Aerospace Corporation Multistage pulse tube coolers

Also Published As

Publication number Publication date
JPS54122449A (en) 1979-09-22
IT7948032A0 (it) 1979-02-16
IT1114963B (it) 1986-02-03
JPS6051624B2 (ja) 1985-11-14
GB2015140A (en) 1979-09-05
GB2015140B (en) 1983-02-02
LU80932A1 (fr) 1979-06-18
DE2806829A1 (de) 1979-08-23
CH624476A5 (fr) 1981-07-31
NL177043B (nl) 1985-02-18
NL7901235A (nl) 1979-08-21
CA1082473A (fr) 1980-07-29
BE874233A (fr) 1979-06-18
FR2417733B1 (fr) 1983-10-21
FR2417733A1 (fr) 1979-09-14
DE2806829C3 (de) 1984-09-20
DE2806829B2 (de) 1981-01-15
NL177043C (nl) 1985-07-16

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